Converter construction and control



" May 20, 1947. H. o. SCHJOUN 2,420,914

CONVERTER CONSTRUCTION AND CONTROL Original Filed Oct. 4, 1940 5 Sheets-Sheet 1 lrmentor 2922s (2 Jazz '01:

(Ittomegs y 1947. H. o. SCHJOLIN 2,420,914

CONVERTER CONSTRUCTION AND CONTROL Original Filed Oct. 4, 1940 5 Sheets-Sheet 2 Snnentor May 20, 1947. H. o. SCHJOLIN I CONVERTER CONSTRUCTION AND CONTROL Original Filed Oct. O 4, 1940 5 Sheets-Sheet 3 2 9 Sckj i (Ittomegs May 20, 1947. H. o. SCHJOLIN CONVERTER CONSTRUCTION AND CONTROL Original Filed 001;. 4, 1940 5 Sheets-Sheet 4 9/2 22; 9 J' :12 john (Iflomegs y 20, 7- H. o. SCHJOLIN 2,420,914

CONVERTER CONSTRUCTION AND CONTROL Original Filed 001;. 4, 1940 5 Shets-Sheet 5 3nnentor ttomegs i atented 29, i4?

CONVERTER CONSTRUCTKON AND CONTROL Hans 0. Schjolin, Birmingham, Mich.', assignor,

by mesne assignments, to General Motors Corporation, Detroit, Mich, a corporation of Delaware Original application October 4, 1940, Serial No. 359,747. Divided and this application April 13, 1943, Serial No. 482,892

. 9 Claims. 1.

This specification is a divisional application of my U. S. Serial Number 359,747, filed October 4, 1940, which matured February 8, 1944, as U. S. 2,341,163.

The invention relates to motor vehicles, more particularly those in which is required a compact grouping of the driving mechanism for large vehicles such as passenger busses, trucks. and tractors.

The invention relates specifically to a form of semi-automatic control whereby the driver, through manipulation of a unitary element, controlling sin'zle operating means, may compel selective drive at either top ratio, or reduction drive. The invention relates thereunder to control devices in which the will of the vehicle operator in selecting ratio is expressed through the agency of fluid pressure servo means, and in particular to servo systems utilizing a single conduit to provide multiple operating characteristics.

The invention likewise relates to a method of organization of the elements of a power plant and associated hydraulic driving mechanism whereby a minimum of points for leakage of hydraulic liquid is attained.

converter providing infinitely variable drive in.

the lower speed ratios and control means therefor embodying interlinked mechanism for establishing converter drive or by-pass drive directly cou-- pling the power to the load. The sealed end construction of Figures 1 and 2 described below is shown in the applicant's Letters Patent, U. S. 2,272,434, filed February 9, 1938, issued February 10, 1942.

Additional advantages appear in the application of interlocking driver controls for the described forms of mechanism whereby prevention of wrong motion is achieved; wherein there is a simple coordination of foot and hand operated elements; and wherein the interlocking means control fluid pressure servo motors compelling change of drive between the converter and drive coupling means at the will of the operator. 1

The subject matter of the present invention is related to my application United States Serial 2 Number 189,596, filed February 9, 1938, in particular the structural drive pattern of Figs. 1 and 2 thereof.

Further objects and advantages appear in the following detailed description given in connection with the accompanying drawings, wherein:

Figure 1 is a schematic view of an installation of the driving portion of my invention, applied to a motor bus chassis, with the power plant arranged transversely at the rear.

Figure 2 is a longitudinal section of the power plant of Figure 1 taken in part section in the longitudinal plane.

Figure 3 shows the sectional detail of the mechanism at 3-3 of Figure 2, with the shifter means engaged for forward drive.

Figure 4 is an enlarged sectional view of the direct drive clutch D of Figure 2.

Figure 5 is a schematic diagram of the operator controls arranged to operate the shifter mechanisms of Figure 2.

Figure 5a is a sectional view of the operator control means for the servo and clutch devices of Figures 2 and 6.

Figure 6 is a modified form of the gearing and converter arrangement of Figure 2 in which the clutches C and D are of the same type, commonly operated and controlled. Figure 7 is a partial section elevation at l-l of Figure 6 of the operating mechanism for the clutches C and D of Figure 6. The arrangement of Figure 6 cmbodies the sealing feature noted in the preamble.

Supplementary Figure 8 is a sectional view of the single operating cylinder of Figure 6 showing the method of obtaining positive neutral.

Referring particularly to Figure 1, the drive arrangement is shown as installed in the rear of a passenger bus with the primary power plant arranged transversely and the output drive in the fore-and-aft plane of the vehicle connected by a short jackshaft 69 to the conventional differential gear and axle drive to the rear wheels. The primary power plant comprises an engine A of suitable type, a clutch C, a clutch D, a turbine type torque converter T as a variable speed transmission, a gear assembly R, an overrunning device F, and an accessory drive mechanism E all mutually coaxial.

The propeller shaft 69 extends forwardly with respect to the vehicle, and downwardly, from a point intermediate the engine A and the torque converter unit T, driving a conventional differential gear G.

In Figure 2 the engine crankshaft is shown at l, mounted to rotate drive shaft 2 splined at 3 3 for slider 4, and splined at 5 for clutch hub 6 and flanged fitting 8 which drives the accessory units.

Sleeve 3 mounted on proper bearings surrounds shaft 2 and is attached to or integral with member l having internal ring of teeth II and external bevel teeth I2. Teeth l3 of slider 4 mesh with teeth so that member Ill, when the jaw clutch thus described is engaged, will be driven 4 at engine speed.

'Output jackshaft 60 rotates on bearing in casing 2|! and is fixed to or integral with bevel gear I meshing with gear I2, transmitting the driving of sleeve 9 to the driving wheels of the vehicle as shown in Figure 1.- Sleeve l5 concentrio with sleeve 9 is mounted to rotate about shaft 2 and carries afiixed gear I6 and roller clutch member l8, the inner end terminating in turbine element 30, which is the output memberof the torque converter unit T.

Roller clutch member 2| is externally splined at 22, the teeth 23 in splines 24 of sleeve 9 being aligned axially and radially therewith. Slider 25 is splined internally at 2|. When the teeth 2| are in mesh with the teeth 23 of the sleeve 3, the output member 2| of the roller clutch-assembly F is released.

When slider 25 is moved to the left, or toward the engine, its teeth 26 also mesh with teeth 28 of gearbody 28 rotating in hearings in the casing 20. Teeth 21 of member 29 constantly mesh with reverse idler gear 32, which in turn meshes with gear l6. When slider 25 isin the righthand position, the driver from sleeve I5 is carried by roller clutch member l8 and 2|, slider 25, teeth 22 and 2|, and sleeve 9. When it is in the left-hand position, the drive is through gears Ill-32, gearbody 29, slider 25, and sleeve 9, yielding reverse drive. Figure 2 shows slider 25 meshed with teeth 22, as when in forward drive the roller clutch F is made active.

art, and are capable of providing multiplication of torque over predetermined speed range.

The three elements of the turbine device, impeller 40, the reaction member 50, and rotor 30, provide torque multiplication so as to impart infinitely variable speed to sleeve l5 from sleeve 34, which revolves at engine speed when clutch C is engaged. As previously described, the pow c: is delivered to jackshaft 60. The infinitely variable speed ratios obtained through the converter T cover a predetermined zone of available ratios depending upon the load and speed ranges required for the service of the vehicle, and no invention is herewith claimed for the torque converter, the form of unit being well known.

With the engagement of clutch D the drive is transmitted from the engine to shaft 60 at the .rollers |9 carried in cage I911, serving to lock the drive for one direction of relative rotation to the outer race |8a and. to release it for the other.

- Roller cage |9a is fixed to rotate with the inner The slider 25 has three operational positions;

at the extreme left its teeth 26 meshing with gear 28 and its teeth 2| meshing with teeth 23 of sleeve 3 to transmit the reverse drive torque from the train |6322| to the final drive shaft 63 through bevel gears |l|4. Its mid-position leaves it carried on teeth 24 of sleeve 9, free of other rotating members. In the right hand position it connects teeth 22 of the roller clutch race ring 2| to teeth 24 of sleeve 9 for providing forward drive.

Hub and flange 6a upon which is formed support 33, delivers the power of the engine from shaft 2, so that pressure plate 36 mounted on 39-6a may engage clutch driven disc 49 having facings 43. Hub 33 carries disc 49 and is splined to hollow shaft 34 connected to or integral with the impeller 43 of the converter T.

Converter blades 50aand 50b shown in elevation in Figure 2 constitute reaction supporting means for the converter T, and may be attached to or integral with the casing 20.

The spinning of impeller 40 circulates the liquid contained in the converter compartment so as to impinge on the blades 3|a, and the blades 53a convert negative to positive force by causing rotation of blades 3|. Specialized forms of the blades and their distribution within the converter compartment are not involved in this invention. The net result is'to apply rotational energy to the rotor 30 attached to sleeve l5, the force being delivered at variable speed ratios.

Such turbine devices are well known in the member l8, and has limited lost motion with respect thereto.

Slider 25 in mid-position demeshes teeth 2|- from the teeth 22 of member 2|, but is partially meshed with teeth 23. This permits the slider 25 to give full release of the roller clutch F when the controls are placed in reverse position.

Figure 4 shows in section the the direct drive clutch D of jaw clutch type. Shaft 2 is splined at 3 to engage mating teeth out on slider 4 which carries direct drive teeth I3. Member l0, which is arranged to drive bevel gear I4, is extended and enlarged so that its internal ring ofteeth I i may mesh with teeth l3 of slider 4.

On a portion extending to the right of slider 4 are out two rings of teeth. 54 and 55. Teeth 54 carry balking ring 53 having limited rotational lost motion in its splining through the teeth53a. Piece 53 is shaped to bear against collar 56 held on the inner portions of teeth Spring 63 exerts constant tension between the slider 4 and the ring 53 so that when teeth l3 and II are disengaged there is always present a slight frictional force between elements 53 and 56.

The upper lip of member 53 is held by spacer 52 and lock ring 52a, preventing the backing off of ring 53 from contact with collar 56.

When the slider 4 is stressed for engagement of teeth l3||, the force of spring 59 is augmented. The differential rotations of shafts 2 and I0 cause ring 53 to be biased rotationally in one direction or another constantly with respect to teeth 55, so that the mechanism tends to reject mesh, the stub ends of teeth 53a. blocking teeth 55 until synchronous speed is reached.

This blocking action occurs whenever the engine speed is greater or less than the speed of shaft I 0. As soon as synchronism is reached, the biasing force between member 56 and ring 53 no longer exists; therefore teeth 55 may pass freely into the spaces of teeth 53a and complete mesh of teeth H and I3 then occurs without clashing. The particular form of constantly loaded synchronizer mechanism in combination drive in direct is believed novel and useful.

The operating mechanism for clutch D of Figure 2 consistsmf yoke 10 of gearbody 4 fixed to shaft 1I mounted-to slide in bosses 12 of casing 20, the shaft collar 13 affording a seat for tension spring 14 arranged to. load to a predetermined degree, the clutch D for engagement. Cross shaft 69 supported in the casing 20, carries arm I having finger 15a adapted to bear against the enlarged end of fork where it is fastened to shaft H. The pivot end b of lever arm 15 is joined to piston rod 16 of servomotor MI, the cylinder I30 of which is attached to the casing 26, and fed by air pipe I24. Biasing spring 11 normally holds piston I48 and rod 16 in the position shown in Figure 2, unless air pressure is admitted to the cylinder I30, whereupon lever 15 is rocked clockwise, the finger 15a relieving the force of spring 11, so that the direct drive clutch loading spring 14 can initiate the action leading to direct drive clutching by teeth I3 and II.

The operating mechanism of clutch C of Figure 2 consists of yoke 44a engaging bearing collar 44 which limits the movement of disc spring 42 for loading presser plate 36. Cross shaft 41 carries lever 46 engaging fork 44a, and pivoted to piston rod I45 of servomotor M--2. As will be described, the servo system is arranged to actuate both servomotors MI and M-2 from a common control means, for prevention of wrong motion, and for economy of parts.

servomotor cylinder I 25 mounted on casing 20, houses piston I52 attached to rod I 45, biasing spring I 5I being normally effective to load clutch C unless fluid pressure is admitted to cylinder I25 from branch pipe I23 connected to main air line I22.

As will be clearly understood from the following description, the fluid pressure main line I22 serves the dual purpose of establishing the loading force for direct drive while relieving the turbine clutzh I C. This simultaneous action shortens the shift interval and assures positive relief of reduction drive before the direct drive torque is established through clutch D.

Figure 5 is a schematic representation of the arrangement of the controls between the driver's compartment, located at the front end of the vehicle, and the power plant compartment, located at the rear end of the vehicle.

Conveniently placed to the hand of the operator is master shift control handle I00 pivoted in fitting I0! attached to the dash. Shaft I02, supported in the fitting, terminates in arm I03 pivoted to clevis I04 attached to vertical rod I05. Below the main floor line belicrank I05, pivoted to the vehicle frame, is attached to rod I05, the opposite arm being attached to longitudinal rod I01 so as to convert the reciprocal movement of the handlever into fore and aft movement of the rod I01.

The power plant, including the power transmitting arrangements, is shown in outline at the left-hand of the drawing, the contour being in accordance with the showing of Figure 1.

Projecting toward the eye of the observer is shaft IIO, likewise shown in Figure 1, and to it is attached arm 0' outside the casing 20 pivoted to rod I09. BellcrankIIlS, pivoted to the frame of the vehicle, transmits the movement of rod I01 to rod I09, so that the shifting movement of the handlever I00 is converted to rocking movement of arm 0' and shaft IIO, which,

as will be seen from Figure 1, may mesh slider 25 with the teeth 2| of ring 2I for forward drive, and mesh teeth 26 with teeth 23 and gear 28 for reverse drive.

It will be observed that all shifts of the handlever I00 will occurv at times when the engine is idling or rotating at low speed.

Air supply tank 200 is shown schematically in the figure, and is maintained with the customarypump X and automatic valve. The main pressure line I20 delivers constant air pressure to space I2I of valve casing 20I, the delivery line I22 of valve casing 20I passing toward the rear of the vehicle, where it is connected to two pipes I23 and I24 feeding servo cylinders I25 and I30.

The shift control pedal I35 is pivoted to the floorboards of the drivers. compartment in an extension of the valve housing 20I as shown in Figure 5. The pedal shaft I36 has aflixed cam I31 with notches I38 and I39 for two positions, the limiting portions of the inner part of the casing 20I compelling the pedal to occupy normally one of the two positions indicated. However, as will be described later, the pedal I35 may be pressed a slight distance downward beyond the position shown in Figure 5a for the purpose to be described in detail following.

In the most elevated position of the pedal I35, control over the transmission apparatus is required to establish direct drive, which will be described as position I. As the porting of the valve mechanism is so arranged with respect to pedal movement, both servo cylinders I25 and I30 are supplied with air pressure from tank 200. The second normal position (II) of pedal I35 is for the purpose of connecting the torque converter unit by engaging clutch 36 and 43 of Figure 2, the valve mechanism in this position being closed so that neither of cylinders I25 and I30 obtain air pressure from tank 200, but are exhausted to atmosphere.

In position III of pedal I35, the valve mechanism. is permitted to deliver a momentary increase in air pressure to line I22 and to both of cylinders I25 and I30 for a purpose to be described later.

Valve member I26 is afilxed to roller I21 and may occupy a high position when the roller is in notch I38 of cam I31, and may occupy a lower position when the roller is in notch I33 of cam I31. These two positions correspond. to torque converter and direct drive respectively. The boss I28 of valve I26 adjacent to roller I21 is fitted to bore I29 of easing 2M and the stem portion of the valve I26 slides within extension I3I of casing 20I. Valve member I26 is drilled out lonitudinally at I32 and at I33. When the valve is pressed down, exhaust port I34 may no longer communicate with the passage I32, and dumbbell vglve I42 closes off release of air by seating in I I.

Valve seat I4! is centrally ported to form a seal with the spherical face of dumbbell valve I42, the other end of which may likewise prevent air from passing through longitudinal passage I32 of valve member I26 to exhaust port I34. Conical spring I43 is seated under the head of dumbbell valve I42 so that the force of the spring may assist the air pressure from space I2I to seat the valve I42 against the valve seat I44. The inner end of the stem of valve member I26 carries spring seat I4I pressed upward by spring I46, which normally exerts compression by resting against the inner face of the valve seat I44, In the position shown in 7 Figure a, the roller I21 is seated in notch I33 of cam I31, and therefore servo pressure line I22 may drain through longitudinal passage I32 in valve member I23 to exhaust port I34.

The operator may depress his heel on the rearward portion of control pedal I35, raising the pedal to osition I and causing roller I21 to occupy notch I39 so that the upper end of the dumbbell valve I42 tends to seal the longitudinal passage I32 and the lower portion of the dumbbell valve is thrust downward and unseats from seat I44, permitting reservoir air pressure to pass through the inner chamber I41, thence through servo line I22 and to cylinders I25 and I3II of Figure 2.

It is stated previously that in the third position a momentary increase of air pressure could be delivered to the cylinders by depressing the pedal to position 111, Under these circumstances the right hand portion of cam I31 may compel a slight unseating of the dumbbell valve I42, the

operator's foot pressure being reacted against by both of springs I43 and I45.

The effect of this operation is to permit spring 14 to load the direct drive slider 4 of Figure 4 by the action of air pressure in cylinder I33. The friction drag element 53 shown in Figure 4 is being constantly loaded; therefore the balking action described preceding in this specification is exerted.

The momentary increase in air pressure has the effect of releasing the converter clutch 36 and 43 so that the turbine connected parts may cease to spin. The handlever I00 may then be moved to forward position, shifting the slider 2I to couple the external ring 2| of the roller clutch to the output connected shaft 9. This operation only requires half a second.

When the pedal I35 is relieved ofthe foot pressure, it springs back to position H, the air pressure being immediately cut off, the converter clutch C being re-engaged, and drive may proceed from here on through the torque converter unit T and through the roller clutch F to shafts 3 and 50.

The operator may manipulate the ratio control pedal I35 at any time to move it between positions I and III, while driving forwardly, it being required, however, that a momentary release of the accelerator be made in order to relieve the driving torque on the teeth of the direct drive jaw clutch I3 and II so that the biasing force of spring 11, shown in Figure 2, may become eifective to set up disengagement.

The valve control in position II relieves the air pressure which otherwise is exerted in holding the converter clutch C disengaged. and the biasing spring I5I located in cylinder I25 may shift the disc spring collar 44 to the right, as shown in Figure 2, to apply the drive'of the engine to the torque converter T, which may now be brought up to operating speed and begin to deliver torque through the roller clutch F to the output or load shaft when the driving parts come up to the speed of the output shaft.

When the vehicle speed or road conditions permit, the driver may simultaneously release the engine accelerator pedal and rock the ratio control pedal I35 with the heel to position I, which opens the valving I42 so as to admit compressed air to both cylinders I25 and I33. This releases the converter clutch C and loads the jaw clutch D for direct drive.

Since the engine under these circumstances is decelerated, the engine connected shaft 2 and plete mesh of teeth I3 and II when the balking action of the friction element 53 ceases. This occurs when reversal of relative motion takes place. It should be observed that the operator may continue to drive at will in direct without freewheeling, and with the turbine connected parts at rest.

The control actions for reverse drive are the same as for starting and forward except for the direction of the movement of the handlever IIIII and the connected parts. More specifically, the utilization of the third position of servo control pedal I35 for administering a momentary increase of air pressure to cylinders I25 and I33, is used, so that the shift to reverse gear is as silent as the shift to forward running through the converter T.

Figure 6 shows a modification of the construction of Figure 2 in which the engine connected shaft I is Joined to output jackshaft 33 by direct drive clutch D of the friction typ and in which clutches C and D are grouped together at the en ine end of the transmission casing 20. This permits the converter unit T to be installed in a sealed housing, greatly simplifying the problem of enclosing a converter compartment against leakage.

Engine connected shaft I and flywheel is support presser plates I5I and I52. Transmission shaft 2 carries splined hub I33 and clutch disc I64 having facings' I54a. Rotating on shaft 2 is hollow shaft 3 carrying splined clutch hub IE5 attached to clutch disc I66 having facings IiGa. Shaft 3 may drive bevel gear I2 meshed with bevel gear I4 attached to shaft 60 either through clutch D, directly driven by the engine, or 'hrough clutch 0 through the torque converter T. Clutch control mechanism is arranged to provide alternate gripping of eithe of clutch discs I64 or I64 to either of shafts 2 or 9 respectively.

Fittings I 61:; bolted to the flywheel at I51c are arranged to restrain the external edges of compound disc spring I", the inner edges of which may be shifted to the right or to the left by a movement of bearing I1 I and sleeve I12 longitudinally through eccentric yoke I13 moved from outside the gearbox. The fulcrum action occurs through studs I13 and members I31a.

Presser plate I52 carries studs I15 passing through apertures I16 in disc I13, the studs carrying'fulcrum ring I11. A fulcrum portion I52a of presser plate I52 aflords bearing opposite the fulcrum point of ring I11.

When the yoke I13 slides the bearing member I 1| to the left, the spring disc I10 exerts a pull on plate IGI through studs I51 against presser plate I 62, clamping clutch disc I66 for rotation with the flywheel Ia; This operation establishes direct drive while allowing the torque converter to idle.

When the yoke I13 and collar I12 are shifted to the right, the fulcrum at I11 and IBM reverses the force of studs I61 and force is transmitted through fittings I310 to clamp clutch disc I64 between flywheel Ia and presser plate Iii. This action disengages clutch D' and couples clutch disc I54, establishing turbine drive between the engine shaft I and hollow shaft 9. It will be seen that this clutching arrangement is operable in the same manner as that of Figure 2, a simple rocking means for shift lever "I attached to eccentric IIII being the only requirement.

It should be noted that the disc spring assembly and operating mechanism rotate with fly- -wheel Ia, and that the longitudinal motion is apdrive or. neutral according to the setting of the mechanism of Figure 8.

It will be noted that in the arrangement of Figures 6 and 7, only one servo cylinder assembly is needed to perform the work of shifting drive between clutch C and clutch D.

Lever I8I is pivoted to piston rod 16a at yoke 1612, the piston M8a sliding in cylinder I3lla mounted on the casin 20. Biasing spring Ila normally loads piston I48a to the end of the cylinder farthest from the eye of the observer in Figure 6. At the far end, pipe fitting I221; opens into the cylinde I30a at I22c, and is joined to pipe I22a, connected to the valve control arrangement of Figures 5 and 5a in place of pipe I22. The single cylinder arrangement provides a useful saving in parts and in sureness 'of operation.

When fluid pressure is admitted to pipe I221; from the valve control of Figure 5a, the clutch D'-is loaded and the clutch C unloaded. When it is relieved by the valve I26 and I42, spring 'I'Ia shifts the piston I48a to the far end of the cylinder I30a, causing the leverage system of Figures 6 and 7 to unload clutch D and to load clutch C for driving through the converter T.

In Figure 8, a supplementary pipe IMb is shown, connected to a relief valve 2H1 operated by lever 2H and by rod I09 of Figure 5, so that when the hand lever I00 is placed in neutral position,the air pressure fed to pipe I22 by valves I26 and I42 is blown off at the mid position of piston IdBa in cylinder I30a. This establishes a balance between the force of spring Na and the air pressure in cylinder I3Ila such that the clutch operating lever I8I and connected parts are positioned for unloading both clutches C and D. This provision of a positive neutral control is not absolutely necessary for idling with no-drive, since the engagement of clutch C, while spinning the converter impeller d0, does not, at ordinary engine idling speeds, furnish sufficient torque to apply other than a small drag component, which, when the vehicle brakes are lightly applied, cannot cause the vehicle to creep forward, even if the gearing be connected for forward or reverse drive.

The above described system has the following advantages:

a. The driver need not use his hands for shifting ratio, except for initiating drive, and for shifting to reverse. He need only use the master shifter pedal-and the regular accelerator and brake pedals. The elimination of the clutch pedal is of utility.

b. The removal of the customary controls clears the space about the driver, who, in a bus, mayhave to make change and operate the bus door.

0. The range of speed at which the shifting action is required is governed entirely by the judgment of the driver, based on his schedule, the bus load and the driving conditions.

d. Synchronization of the direct drive jaw clutch occurs easily under all operating conditions, because of the preloading and control arrangement described.

e. The drive of the engine is automatically released at idling of the engine, and it is diificult to stall the engine since the torque characteristic of the converter diminishes at engine stalling speeds.

,f. The driver does not have to set the hand lever in neutral with each vehicle stop, and can pick up drive in "low" by a mere rocking of the master control pedal.

The invention is described in specific form in the present embodiment, and it is to be understood that this is purely explanatory and not to be taken in any limiting sense, since various changes in the parts, construction and operation may be effected without departure from the full intent and scope of the invention, as defined in the appended claims.

I claim:

1. In driving mechanism for vehicles, a power plant driving arrangement embodying an engine and power shafting connected to drive in one plane, and final drive shafting arranged to deliver output torque in a plane at right angles to said first plane, the centerlines of said shafting intersecting an engine shaft carrying input torque, a hollow shaft surrounding said engine shaft for a part of its length and adapted to drive said final drive shafting, directly through angular gear coupling a torque converter arranged to transmit power from said power shafting to said hollow shaft, and a common housing forall of said shafting and said torque converter effective to enclose all of the torque transmitting parts-except where the power shafting and said final drive shafting enter said housing.

2. In power controls, in combination, a motor vehicle, an engine, a first shaft connected directly to said engine, a second shaft connected directly to the vehicle load, mating positive clutch jaws adapted to couple said shafts, a constantly loaded friction element adapted to prevent, or to permit, mesh of said jaws in accordance with synchronous speeds of the two shafts, a control mechanism for engaging and disengaging said jaws embodying a loading means of predetermined force, an actuating means for said mechanism including a biasing device of superior force to that of said loading means, and normally active to hold said loading means from being exerted on said mechanism, a manually operable pedal, and a power means controlled by movement of said pedal arranged to overcome said biasing means and permit said loading means to become effective upon said mechanism to load said jaws for engagement, whereafter said friction element permits said jaws to engage at synchronous speed.

3. In motor vehicle transmission devices, in combination, an engine connected shaft, a concentric driven sleeve, a load shaft, a gearing mechanism, a fluid turbine power transmission unit, and a, transmission casing apertured at one end for entry of the engine connected shaft and concentric driven sleeve, and apertured at a point at right angles to and in the same plane as the said engine shaft for entry of the said load shaft, the said plane including the centerlines of said shafts and sleeve, said casing entirely enclosing the gearing and the said fluid turbine unit against leakage of fluid except at the aforementioned points of entry of said engine connected shaft and said load shaft.

4. In motor vehicle controls, in combination, a driving shaft, a final drive shaft angularly intersecting said driving shaft, coupling means for said ll shafts including a direct drive coupling clutch adapted to connect the drive of said shafts, and including a secondary load shaft concentric with said driving shaft geared to transmit torque directly from said driving shaft to said final drive shaft and coupled to said driving. shaft at l-to-l ratio by said clutch, a reduction speed ratio unit arran ed to be coupled to transmit torque from said drivingshaft to said load shaft, a reductiondrive' selecting clutch for said unit, a drive-determining clutch mechanism including said first named clutch for coupling said driving shaft and said load shaft, 9. fluid pressure source, a fiuid pressure valve means controlling the fiow from said source. fluid pressure motor means fed by said valve means and arranged to actuate said mechanism when said valve means admits fluid pressure from said source. and a manuallv operable control for said-valve means effective to ap ly and exhaust fiuidpressure to and fromsa d motor means for alternatin the drive of said clutches in direct or reduction speed ratio respectively.

5. In motor vehicle controls, in comb nation. a transmission assemb coupling a driving shaft and a final drive-shaft ancu arlv intersecting said driving shaft. said assembl including a direct drive cou ling clutch to connect the drive of sa d shafts and a concentric load shaft earedto transmit toroue directly between the driving and final drive shafts by the said clutch coupling the said load shaft to the driving shaft at l-to-l ratio. a reduction speed ratio unit arran ed to be cou led for transmitting toroue from said driving shaft to saidload shaft and having a reductiondrive determining clutch actuated by drive actuating clutch mechanism likewise actuating said firstnamed clutch for coupling said driving and said load shafts. power means effective to actuate said mechanism for alternating the drive of said clutchesfor either direct coupled drive between said concentric driving and load shafts or reduction drive therebetween, and manual control means for said power means movable to one position to apply the power of said power means for drive by the said second namedclutch and movable from the said first-named position to a second position in which the power means is rendered ineffective whereby the said first named clutch is madeoperative to engage said driving and load shafts by the actuation of said mechanism.

6. In power plant driving arrangements, a motor vehicle having a transversely mounted engine driving concentrically arranged power and load shafts coupled by a variable speed transmission mechanism. and final drive shafting arranged to deliver output torque, said final drive shafting having a common centerline intersection with the torque transmitting parts of the said driving assembly except where the power shaft and final drive shaftings enter said housing.

7. In motor vehicle driving arrangements, in combination, an engine, an engine-driven shaft, a concentrically driven sleeve, a load-shaft, a variable speed transmission assembly coupling said engine-driven shaft and sleeve including a fluid turbine drive device, and a casing apertured at one end for the engine connected shaft and said sleeve, and apertured at a point for angular entry therein in a' plane common to said concentric sleeve and shaft for entry of said load shaft, said casing enclosing the said transmission assembly.

and the said fluid drive device except for the points of entry of said engine and load shafts.

8. In a motor vehicle, the combination of a transversely mounted power plant including an engine, a variable speed transmission driving assembly and a final drive shaft; a power shaft driven by said engine, the final drive shaft lying in a common plane with said power shaft, the variable speed driving assembly being concentric with said power shaft and coupling same through sleeving and gearing with the said final drive shaft, the said power shaft extending through the driving assembly and being coupled thereto at a pointremote from said engine, and a power accessory drive means attached to said power shaft beyond the point of said coupling with said power shaft and farther remote from the said engine.

9. An arrangement of power drive consisting of a power transmitting assembly having an angularly disposed shaft, housing means for said assembly comprising a first compartment, an intermediate compartment providing support for said angularly placed shaft and a third compartment adjacent said intermediate compartment, a power input drum driven by said engine and located in said first compartment, a plurality of clutches adapted to be selectively coupled to said drum and located in said first compartment, a power shaft concentric with said drum and said clutches and adapted to drive said angularly placed shaft when one of said clutches is coupled to said drum, a load shaft concentric with said power shaft and extending into said intermediate compartment, a variable speed ratio transmission located in said third compartment and having shaft members providing output coupling to said load shaft and input coupling with the other of said clutches, and actuating means for selective operation of said clutches and said transmission mounted on and supported by said compartments.

HANS O. SCHJOLIN.

REFERENCES CITED The following references are of record in the file of this patent:

UNITED STATES PATENTS 

